CN107178492B

CN107178492B - Control valve of variable displacement compressor

Info

Publication number: CN107178492B
Application number: CN201610139617.0A
Authority: CN
Inventors: 汪立新; 王正伟
Original assignee: Zhejiang Sanhua Automotive Components Co Ltd
Current assignee: Zhejiang Sanhua Automotive Components Co Ltd
Priority date: 2016-03-11
Filing date: 2016-03-11
Publication date: 2019-12-13
Anticipated expiration: 2036-03-11
Also published as: CN107178492A

Abstract

the invention discloses a control valve of a variable displacement compressor, wherein a valve body of the control valve is provided with a suction inlet, a crank chamber port, a discharge port and a first valve port for conducting the discharge port and the crank chamber port when the control valve is opened; the control valve is also internally provided with a pressure sensing part, a coil part and a core iron part, and a pressure sensing element of the pressure sensing part senses pressure deformation of a suction inlet and can drive a valve core of the control valve to move so as to adjust the opening degree of the first valve port; the pressure sensing element is arranged in the coil shell of the coil part; the core iron part comprises a transmission rod which is fixed with the movable core iron and moves along the axial direction of the valve cavity, the transmission rod is abutted against the pressure sensing element, the pressure sensing element deforms to drive the transmission rod and the movable core iron to move, and the movable core iron drives the valve core to move so as to adjust the opening degree of the first valve port. In this scheme, the pressure sensing element is arranged in the coil shell, the top of the coil shell is used for arranging the plug and the like, and the inner space of the coil shell has no other function, so that the space in the coil shell can be fully utilized, the control valve can be more miniaturized, and the miniaturization of the compressor is promoted.

Description

control valve of variable displacement compressor

Technical Field

The invention relates to the technical field of control valves, in particular to a control valve of a variable displacement compressor.

background

the piston of the variable displacement compressor is connected to a rocker plate attached to a rotary shaft rotationally driven by an engine, and the stroke of the piston is changed by changing the angle of the rocker plate, thereby adjusting the discharge amount of refrigerant. The angle of the rocker plate is continuously changed by introducing a part of the discharged refrigerant into the closed crank chamber and changing the balance of pressures applied to both surfaces of the piston. The pressure in the crank chamber is controlled by a control valve provided between the discharge chamber and the crank chamber or between the crank chamber and the suction chamber of the compressor.

Referring to fig. 1, fig. 1 is a schematic structural diagram of a control valve of a variable displacement compressor in the prior art.

The control valve includes a valve body 10 and a coil part 3 which are vertically arranged, and the valve body 10 and the coil part 3 are connected by a connecting member 48, as viewed in fig. 1.

The valve body 10 is provided with a valve core 38 and a working rod 36 connected with the valve core 38, the lower end of the working rod 36 contacts a second plunger 68, and a pressure sensing diaphragm 65 is arranged below the second plunger 68. The second plunger 68 is located within the connecting member 48 and has a flange at its upper portion with a spring 74 pre-compressed between the flange and the connecting member 48.

A discharge port Pd communicating with the compressor discharge chamber and a suction port Ps communicating with the compressor suction chamber are opened in the peripheral wall of the valve body 10, and a crank chamber port Pc communicating with the crank chamber is provided in the top of the valve body 10.

The coil portion 3 includes a bobbin 60 and an electromagnetic coil 62 wound around the bobbin 60. The coil part 3 has a core iron part installed therein, including the moving core 56 and the first plunger 66, the first plunger 66 has a shaft 88 extending downward fixed thereto, and a pre-compressed spring 75 is provided between the shaft 88 and the bottom of the core iron part.

The working process of the control valve is as follows:

the compressor is not started:

the solenoid section 3 is not energized, and if the air conditioner for the vehicle is used for the air conditioner for the vehicle, that is, the air conditioner for the vehicle is not operated, there is no attraction force between the moving core 56 and the plungers 58 (the first plunger 66, the second plunger 68). Since the pressure of the suction port Ps is high, the first plunger 66 is moved downward by the pressure against the pressure of the spring 75; the second plunger 68 is urged away from the first plunger 66 by the spring 74, against the force of the spring 46, to move the operating rod 36 and the spool 38 upwardly, opening the valve port 32 and communicating the crank chamber port Pc with the exhaust port Pd. The refrigerant discharged from the discharge chamber of the compressor can flow from the crank chamber port Pc to the crank chamber through the valve port 32, and therefore, the crank chamber pressure rises and the compressor performs the minimum capacity operation.

The compressor just starts:

The coil section 3 is energized to provide the maximum control current to the electromagnetic coil 62 and the first plunger 66 attracts the second plunger 68 against the force of the spring 74. The second plunger 68 abuts against the pressure sensing diaphragm 65, the pressure of the suction port Ps is high, the integral plunger 58 moves downward, and the valve element 38 is pushed down by the spring 46 to close the valve port 32. At this time, the operating lever 36 is separated from the second plunger 68.

The compressor normally works after being started:

The suction chamber pressure becomes low, the suction port Ps pressure becomes low, the pressure-sensitive diaphragm 65 is displaced upward, and the second plunger 68 again abuts against the operating lever 36. At this time, when the control current supplied to the electromagnetic coil 62 of the electromagnetic unit 3 is reduced in accordance with the set temperature of the air conditioner, the second plunger 68 and the first plunger 66 are integrally kept in the attracted state, and move upward to a position where the suction port pressure is balanced with the load of the springs 46, 74, and 75 and the suction force of the electromagnetic unit 3. As a result, the valve element 38 is pushed up by the second plunger 68, and the valve port 32 is set to the opening degree, the refrigerant in the discharge port Pd is controlled to flow at a flow rate corresponding to the opening degree and enters the crank chamber, and the compressor is operated at a capacity corresponding to the control current.

the technical problems of the scheme are as follows: the valve body structure of the control valve is large, which is not beneficial to the miniaturization of the compressor.

Disclosure of Invention

To solve the above problems, the present invention provides a control valve of a variable displacement compressor, which is reduced in size to facilitate miniaturization of the compressor.

The specific scheme is as follows:

The control valve of the variable displacement compressor is provided with a suction inlet communicated with a suction chamber of the compressor, a crank chamber port communicated with a crank chamber, a discharge outlet communicated with a discharge chamber of the compressor, and a first valve port for communicating the discharge outlet and the crank chamber port when the control valve is opened;

the control valve is also provided with a pressure sensing part, a coil part and a core iron part, wherein the pressure sensing part comprises a pressure sensing element, and the pressure sensing element senses the pressure deformation of the suction inlet and can drive a valve core of the control valve to move so as to adjust the opening degree of the first valve port;

The pressure sensing element is arranged in a coil shell of the coil part;

the core iron part comprises a transmission rod which is fixed with the movable core iron and moves along the axial direction of the valve cavity, the transmission rod is abutted against the pressure sensing element, the pressure sensing element deforms to drive the transmission rod and the movable core iron to move, and the movable core iron drives the valve core to move so as to adjust the opening degree of the first valve port.

In this scheme, set up the pressure sensing component of pressure sensing portion in coil shell, coil shell's shell top is used for setting up plug etc. and its inner space does not have other effects, locates the pressure sensing diaphragm in it, can make full use of coil shell inside space, under the condition that does not change coil portion volume, need not occupy the space of coil portion below part to make whole control valve can be more miniaturized, thereby promote the miniaturization of whole compressor.

Optionally, the transmission rod and the moving core are provided with a passage to communicate the suction port and the pressure sensing element.

Optionally, the passage comprises a first radial hole and a first axial hole which are communicated with each other and arranged on the movable core iron, and a second radial hole and a second axial hole which are arranged on the transmission rod;

The first radial hole is positioned at one end of the movable core iron, which is close to the valve core, and is communicated with the suction inlet which is arranged on the valve body in the radial direction; one end of the transmission rod is inserted into the first axial hole, and the second axial hole is communicated with the first axial hole; the second radial hole is formed in one end, abutted to the pressure sensing element, of the transmission rod.

Optionally, the pressure sensitive element is a pressure sensitive film.

Optionally, the pressure sensing portion still includes the pressure sensing shell, still be equipped with the core iron sleeve in the control valve, set up in the core iron sleeve move core iron and quiet core iron, pressure sensing shell lower part opening just is located in the coil shell, the core iron sleeve has the sleeve flanging, pressure sensing shell opening has the shell flanging, the pressure sensing diaphragm press from both sides tightly all around in the sleeve flanging with between the shell flanging.

Optionally, the pressure sensing membrane seals the opening of the pressure sensing housing, and the cavity of the pressure sensing housing is a vacuum cavity.

optionally, be equipped with the bracing piece in the pressure sensing shell and be fixed in the supporting seat at pressure sensing shell top, pressure sensing diaphragm with the precompression has pressure sensing spring between the supporting seat, pressure sensing spring suit in the bracing piece, the bracing piece can peg graft in axial displacement in the supporting seat, the bracing piece butt in pressure sensing diaphragm.

Optionally, the pressure sensing element is a bellows.

Optionally, the pressure sensing part further comprises a pressure sensing shell, the control valve is further provided with a core iron sleeve, the lower portion of the pressure sensing shell is provided with an opening and is arranged in the coil shell, the corrugated pipe is arranged at the top of the pressure sensing shell, the edge of the lower end opening of the pressure sensing shell is in butt joint with the edge of the core iron sleeve, and the movable core iron and the static core iron of the core iron part are arranged in an installation cavity formed after butt joint.

Optionally, the interior of the bellows is a vacuum chamber.

Optionally, the top of pressure sensing shell is equipped with the supporting seat, the supporting seat has towards the extension rod that core iron extends, bellows cover is located the extension rod.

Optionally, the pressure sensing portion further comprises a pressure sensing spring, and the pressure sensing spring is arranged in the corrugated pipe in a pre-compression mode so as to abut against the transmission rod.

Optionally, one end of the valve core, facing the core iron part, is directly jointed with a component on the valve core to form a second valve port;

The valve core is provided with a valve core axial hole which is a through hole, and when the valve core is separated from a component positioned on the valve core, the second valve port is opened so as to communicate the crank chamber port and the suction port.

drawings

FIG. 1 is a schematic diagram of a variable displacement compressor control valve according to the prior art;

FIG. 2 is a schematic structural diagram of a first embodiment of a control valve of a variable displacement compressor provided in accordance with the present invention, illustrating the operation of the control valve when the compressor is off;

FIG. 3 is a schematic view of the valve body portion of FIG. 2;

FIG. 4 is a state of operation of the control valve of FIG. 2 immediately after the compressor is started;

FIG. 5 is a schematic view of the valve body portion of FIG. 4;

FIG. 6 is a view showing an operation state of the control valve of FIG. 2 in a normal operation of the compressor;

FIG. 7 is a schematic view of the valve body portion of FIG. 6;

FIG. 8 is a schematic structural view of the coil housing of FIG. 2;

FIG. 9 is a schematic structural diagram of a second embodiment of a control valve of a variable displacement compressor provided in accordance with the present invention, illustrating the operation of the control valve when the compressor is off;

FIG. 10 is a schematic view of the valve body portion of FIG. 9;

FIG. 11 is the control valve of FIG. 9 in an operational state just after the compressor has been started;

FIG. 12 is a schematic view of the valve body portion of FIG. 11;

FIG. 13 is a view showing an operation state of the control valve of FIG. 9 in a normal operation of the compressor;

fig. 14 is a schematic view of the valve body portion of fig. 13.

the reference numerals in fig. 1 illustrate:

10 a valve body portion; 3 coil parts; 62 an electromagnetic coil; 38 a valve core; 36 working rods; 66 a first plunger; 68 a second plunger; 58 plunger piston; 48 a connecting member; 46. 74, 75 springs; 88 shafts;

A Ps suction inlet; a Pd discharge port; pc crank chamber port;

32 valve port

Reference numbers in fig. 2-14 illustrate:

1, a coil shell; 2 a pressure sensitive housing; 3, supporting a seat; 4 a pressure sensing spring; 5, supporting the rod; 6a fourth O-ring; 7 a magnetizer; 8, pressure-sensitive film; 8' a bellows; 9 a first mandrel collar; 10 supporting a spring; 11a transmission rod; 11a second axial hole; 11b a second radial hole; 12, static core iron; 13 a coil winding; 14, a coil framework; 15 a second core sleeve; 15' core iron sleeve; 16 moving core iron; 16a first axial bore; 16b a first radial hole; 17 a coil protecting case; 18 a connecting seat; 19 a third O-ring; 20 a valve body; 21a valve core; 21a spool axial bore; 21b a valve core radial hole; 22 a first O-ring; 23 discharge screen; 24 a bottom spring; 25 a second O-ring; 26 crank chamber screens; 27, a base.

Detailed Description

In order to make the technical solutions of the present invention better understood by those skilled in the art, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.

example 1

referring to fig. 2, fig. 2 is a schematic structural diagram of a first embodiment of a control valve of a variable displacement compressor according to the present invention, illustrating an operating state of the control valve when the compressor is turned off; fig. 3 is a schematic view of the valve body portion of fig. 2.

the control valve, according to the view angle of fig. 2, arranges the coil part and the valve body part from top to bottom in sequence, and the coil part and the valve body part can be connected by the connecting seat 18, but obviously, the connection is not necessary, and the direct connection is also feasible; the coil part is provided with a corresponding core iron part. In this context (including embodiment 2), the upper direction is the direction toward the top of the coil part, and the lower direction is the direction toward the bottom of the valve body part.

the valve body 20 of the valve body is provided with a suction port Ps communicated with the suction chamber of the compressor, a crank chamber port Pc communicated with the crank chamber, and a discharge port Pd communicated with the discharge chamber of the compressor, in this embodiment, the suction port Ps, the crank chamber port Pc, and the discharge port Pd are all radially disposed on the peripheral wall of the valve body 20 and communicated with the valve cavity. In addition, the suction port Ps, the discharge port Pd, and the crank chamber port Pc are distributed from top to bottom, and a sealing groove may be formed on the outer circumference of the valve body 20 to mount the first O-ring 22 and the second O-ring 25, which are respectively located between the suction port Ps and the discharge port Pd, and between the discharge port Pd and the crank chamber port Pc, so as to isolate the suction port Ps from the discharge port Pd, and the discharge port Pd from the crank chamber port Pc. A discharge screen 23 and a crank chamber screen 26 may be provided at the discharge port Pd and the crank chamber port Pc to filter the refrigerant and prevent impurities from entering the inside of the valve body 20.

As shown in fig. 3, the valve body 21 moves upward by a predetermined distance to close the first port b, and moves downward by a predetermined distance to open the first port b, and when the first port b is connected, the discharge port Pd and the crank chamber port Pc can be connected. As shown in fig. 3, the valve body 21 is provided with a valve body axial hole 21a, and a valve body radial hole 21b communicating with the valve chamber is provided at a position close to the discharge port Pd, and the valve body radial hole 21b communicates with both axial holes of the valve body 21.

when the first valve port b is opened, the crank chamber port Pc can be communicated with the discharge port Pd through the valve chamber, the valve core axial hole 21a, the valve core radial hole 21b, the valve chamber, and the first valve port b in sequence. The bottom of the valve core 21 is provided with a bottom spring 24, and in fig. 3, the valve body 20 is processed to be axially penetrated for the convenience of processing, and at this time, a base 27 is additionally provided at the bottom of the valve body 20, and the bottom spring 24 may be pre-compressed between the bottom of the valve core 21 and the base 27, and its restoring force is used as a force for closing the first valve port b.

the core iron part comprises a movable core iron 16 and a static core iron 12 which are matched, the lower end of the movable core iron 16 can be abutted against the valve core 21 under a normal state (except a state that the compressor is just started), the movable core iron 16 is fixedly provided with an axially extending transmission rod 11, and the transmission rod 11 and the movable core iron 16 synchronously act. In fig. 2, the moving core 16 is provided with a first axial hole 16a, and the lower end of the transmission rod 11 is inserted into the first axial hole 16a and is in interference fit to realize fixation. In addition, the static core iron 12 is also provided with an axial through hole, and the transmission rod 11 fixed on the lower dynamic core iron 16 penetrates through the axial through hole. In order to improve the magnetic circuit, a magnetic shielding sheet can be nested between the static core iron 12 and the moving core iron 16.

When the coil winding 13 of the coil part is electrified, the movable core iron 16 and the static core iron 12 can be attracted, and when the coil winding is not electrified, the movable core iron and the static core iron are separated. The coil part specifically comprises a coil framework 14, an enameled wire is wound on the coil framework 14 to form a coil winding 13, and the core iron part is basically positioned in an inner cavity of the coil framework 14.

The control valve is also internally provided with a pressure sensing part, the pressure sensing part is arranged in the coil shell 1 of the coil part, the top of the shell of the coil shell 1 is used for installing parts such as a plug and the like, and the lower part of the shell is mainly formed in an installation space for installing the coil framework 14 and the coil winding 13, so that the pressure sensing part is arranged in the top of the shell of the coil shell 1, namely in the coil shell 1 and above the coil winding 13.

As shown in fig. 2, the pressure sensing portion includes a pressure sensing element, which is specifically a pressure sensing film 8 in this embodiment, and in order to facilitate positioning of the pressure sensing film 8, the pressure sensing portion is provided with a pressure sensing housing 2, the pressure sensing housing 2 is provided with an opening facing the core iron portion, the edge of the opening is provided with a housing flange, and the pressure sensing housing 2 can be formed by sheet stretching. The core iron part is arranged in the core iron sleeve, the edge of the core iron sleeve facing the pressure sensing part is correspondingly provided with a sleeve flanging, and the periphery of the pressure sensing diaphragm 8 is clamped between the sleeve flanging and the shell flanging. The arrangement is simple and reliable.

it should be noted that the core sleeve may be an integral type or a split type, and in order to facilitate installation, a split type structure is adopted in this embodiment, as shown in fig. 2, a first core sleeve 9 and a second core sleeve 15 which are distributed up and down are butted to form an installation cavity for accommodating the static core 12 and the dynamic core 16. The sleeve flanging matched with the shell flanging is arranged on the first core iron sleeve 9 arranged close to the pressure sensing shell 2.

In addition, the pressure sensing shell 2 is convenient to form a vacuum cavity, and the pressure sensing diaphragm 8 can be welded between the sleeve flanging and the shell flanging in a vacuum state, so that the vacuum cavity is formed after the pressure sensing diaphragm 8 seals the opening of the pressure sensing shell 2. When pressure sensing diaphragm 8 warp, the volume of 2 inner chambers of pressure sensing shell can change, if there is the air, the air is applyed the power that is applied to pressure sensing diaphragm 8 and can be changed correspondingly, is difficult for controlling pressure sensing diaphragm 8's deflection, and forms the vacuum back, then can avoid this problem to control the displacement of transfer line 11 more accurately, then the displacement that transmits for case 21 is also more accurate, makes the aperture adjustment of first valve port b have higher precision.

One end of the transmission rod 11 is abutted against the pressure sensing membrane 8, and when the pressure sensing membrane 8 deforms, the transmission rod 11 moves axially correspondingly. The driving rod 11 and the pressure sensing diaphragm 8 are tightly abutted mainly by a supporting spring 10, in fig. 2, the supporting spring 10 is arranged between a static core iron 12 and the driving rod 11, specifically, the inner wall of the upper end of the static core iron 12 is provided with a step, the upper end of the driving rod 11 is provided with a radial flange, and the supporting spring 10 is pre-compressed between the flange of the driving rod 11 and the step surface of the upper end of the static core iron 12. The supporting spring 10 mainly applies the abutting force of the abutting transmission rod 11 to the pressure sensing diaphragm 8, and the arrangement position is not limited thereto, even the supporting spring 10 is not necessary, for example, the pre-tightening force of the bottom spring 24 is designed reasonably, and the force of abutting the transmission rod 11 to the pressure sensing diaphragm 8 can also be provided. Of course, when the valve core 21 moves upwards to the limit position, no upward force is provided to the transmission rod 11, generally speaking, the attraction force of the movable core iron 16 when the transmission rod 11 needs to continue to move upwards can also ensure that the transmission rod 11 moves upwards (the just starting state mentioned below), but the existence of the supporting spring 10 can ensure that the transmission rod 11 can continue to move upwards according to the requirement, which is beneficial to reducing the difficulty of electromagnetic control.

in order to provide a force for depressing the valve element 21, a pressure-sensitive spring 4 is further provided, and the pressure-sensitive spring 4 is precompressed between the pressure-sensitive housing 2 and the pressure-sensitive diaphragm 8. The pressure sensing spring 4 can also make the pressure sensing diaphragm 8 always abut against the transmission rod 11 and the pressure sensing diaphragm 8 can return.

Specifically be equipped with supporting seat 3 and bracing piece 5 in pressure sensing shell 2, as shown in fig. 2, the top of pressure sensing shell 2 is fixed in the pressure equipment of supporting seat 3 to reserve in supporting seat 3 and have the guiding hole, 5 one ends nestings of bracing piece are in the guiding hole, make bracing piece 5 can axial displacement. The pressure sensing spring 4 is sleeved on the support rod 5 and is abutted between the flange at the other end of the support rod 5 and the support seat 3. Thus, the pressure sensing spring 4 tightly supports the supporting rod 5 on the pressure sensing diaphragm 8, i.e. the supporting rod 5 and the transmission rod 11 tightly support the two sides of the pressure sensing diaphragm 8 respectively. The support rod 5 enables the force of the pressure sensing spring 4 to act on the pressure sensing diaphragm 8 more uniformly, and also plays a role in guiding the pressure sensing spring 4 to be stable. The support base 3 provides a space for inserting the support rod 5, which is more convenient to install than the support base directly installed on the pressure-sensitive housing 2.

the pressure sensing diaphragm 8 is required to sense the pressure of the refrigerant in the suction port Ps to adjust the opening degree of the first valve port b according to the pressure. In the scheme, the pressure sensing diaphragm 8 is arranged at the top in the coil part coil shell 1, the suction inlet Ps is arranged at the lower valve body part, and in order to enable the refrigerant to be conducted to the position of the pressure sensing diaphragm 8 through the suction inlet Ps, the transmission rod 11 and the movable core iron 16 are provided with passages to communicate the suction inlet Ps and the pressure sensing diaphragm 8.

As shown in fig. 2 in particular, the passage comprises a first radial hole and the first axial hole 16a which are communicated with each other and are provided in the moving core 16, and a second radial hole 16b11b and a second axial hole 11a which are provided in the driving rod 11;

The first radial hole is positioned at one end (lower end) of the movable core iron 16 close to the valve core 21, and because the movable core iron 16 needs to be abutted against the valve core 21, the lower end of the movable core iron 16 is directly inserted into the valve cavity, and the first radial hole is arranged at the lower end of the movable core iron and can be communicated with a suction inlet Ps radially arranged on the valve body 20 through the valve cavity; one end of the transmission rod 11 is inserted into a first axial hole 16a of the movable core iron 16, and the second axial hole 11a is communicated with the first axial hole 16 a; a second radial hole 16b11b is opened at one end of the driving rod 11 abutting against the pressure sensing diaphragm 8.

Thus, the suction port Ps sequentially passes through the valve cavity of the valve body portion, the first radial hole, the first axial hole 16a, the second axial hole 11a, the second radial hole 16b11b and the cavity at the upper end of the stationary core 12 and is communicated to the pressure sensing diaphragm 8, the pressure of the refrigerant of the suction port Ps is transmitted to the pressure sensing diaphragm 8, and when the pressure sensing diaphragm 8 deforms under the pressure action of the suction port Ps, the pressure sensing diaphragm can drive the transmission rod 11 to move axially, and then the valve core 21 abutted to the movable core 16 is driven to move axially.

The passage for communicating the suction inlet Ps and the pressure sensing diaphragm 8 is arranged on the movable core iron 16 and the transmission rod 11, so that the processing is easy, the suction force and the suction action of the core iron are not influenced, and the smooth communication between the pressure sensing diaphragm 8 in the coil shell 1 and the suction inlet Ps of the valve body part below is realized. It should be understood that other communication means may be used, for example, a passage communicating with the valve cavity is formed in the core sleeve, or a passage communicating with the valve cavity is formed in the coil housing 1 of the coil portion, etc., but it is obviously easier to form the passages in the moving core 16 and the driving rod 11.

In addition, the control valve of the present embodiment is further provided with a second port a, and as shown in fig. 3, the second port a is formed at a position where the spool 21 and the moving core 16 are coupled. The valve body axial hole 21a is an axial through hole, and when the second valve port a is opened, the suction port Ps and the crank chamber port Pc can be communicated with each other.

the operation of the control valve in this embodiment can be understood with reference to fig. 2, 3 and 4-7, where fig. 4 is the operation of the control valve in fig. 2 at the beginning of the compressor start; FIG. 5 is a schematic view of the valve body portion of FIG. 4; FIG. 6 is a view showing an operation state of the control valve of FIG. 2 in a normal operation of the compressor; fig. 7 is a schematic view of the valve body portion of fig. 6.

When the compressor is not started:

When the coil is not electrified, the elastic force of the pressure sensing spring 4 overcomes the resistance of the supporting spring 10 and the bottom spring 24, so that the transmission rod 11 and the movable core iron 16 are far away from the static core iron 12 to the maximum displacement position, the lower end part of the movable core iron 16 pushes the valve core 21 downwards, and the first valve port b is fully opened. At this time, the discharge port Pd and the crank chamber port Pc are communicated in the valve body 20.

When the compressor is started:

When the air temperature drops, the refrigerant in the crank chamber of the compressor is liquefied and accumulated. At this time, the compressor is started, the coil is electrified with large current to generate electromagnetic force, so that the moving core iron 16 approaches to the static core iron 12, at this time, the pressure of the suction inlet Ps is large, the pressure of the suction inlet Ps and the transmission rod 11 jointly push the pressure sensing diaphragm 8, the moving core iron 16 moves upwards for a certain distance and does not tightly abut against the valve core 21, the valve core 21 moves in the same direction under the action of the bottom spring 24, so that the first valve port b is completely closed, the discharge port Pd is disconnected from the crank chamber port Pc, and the refrigerant in the discharge chamber cannot flow to the crank chamber.

The distance for moving the core iron 16 upwards needs to satisfy the following conditions: is disengaged from the valve spool 21, thereby opening the second port a to the maximum position. The suction port Ps communicates with the crank chamber port Pc, and the liquid refrigerant in the crank chamber is vaporized and flows into the suction chamber of the compressor through the crank chamber port Pc, the valve chamber, the valve body axial hole 21a through which the valve body 21 passes, the second valve port a, the valve chamber, and the suction port Ps. In the process of discharging the liquid refrigerant, the pressure of the suction chamber and the crank chamber gradually decreases, the pressure of the suction port Ps received by the pressure sensing diaphragm 8 decreases, and the movable core iron 16 moves downwards along with the pressure sensing diaphragm under the action of the pressure sensing spring 4. When the liquid refrigerant is discharged, the movable core iron 16 and the valve core 21 tightly abut again, and the second valve port a is closed.

Through setting up second valve port a, can accomplish the gasification of liquid refrigerant and discharge fast, make the compressor get into normal operating condition fast.

the compressor is in a normal working state after being started:

The opening degree of the first valve port b is controlled by appropriately controlling the energization amount of the coil to vary the electromagnetic force, i.e., by appropriately adjusting the position of the movable core iron 16 using the electromagnetic force, so as to achieve a desired discharge amount.

In addition, when the current is constant, the pressure sensing diaphragm 8 senses the pressure of the suction port Ps to control the opening degree of the first valve port b. When the cooling load becomes larger and the pressure of the suction port Ps becomes larger, the upward acting force applied to the pressure sensing diaphragm 8 increases, the valve element 21 moves upward along with the core iron 16, the opening degree of the first valve port b becomes smaller, the refrigerant flowing into the crank chamber decreases, the discharge amount of the compressor increases, and the pressure of the suction port Ps gradually decreases to the set pressure. On the contrary, when the cooling load becomes smaller and the pressure of the suction port Ps becomes smaller, the upward acting force applied to the pressure sensing diaphragm 8 is reduced, the valve element 21 moves down along with the core iron 16, the opening degree of the first valve port b becomes larger, the refrigerant flowing into the crank chamber is increased, the discharge amount of the compressor is reduced, and the pressure of the suction port Ps is gradually increased to the set pressure.

compared with the background art, the control valve has the following technical advantages:

One, set up pressure sensing diaphragm 8 of pressure sensing portion in coil housing 1, because the shell top of coil housing 1 is used for setting up plug etc. and its inner space does not have other effects, so can locate pressure sensing diaphragm 8 in coil housing 1's headspace, with the inside space of make full use of coil housing 1, under the condition that does not change coil portion volume, need not occupy the space of coil portion below part, thereby make whole control valve can more miniaturize, thereby promote the miniaturization of whole compressor.

In this case, the transmission rod 11 not only serves as a guide for the movement of the movable core 16, but also has an important function of transmitting the deformation of the pressure-sensitive element located above to the movable core 16 and thus to the valve element 21.

In addition, in the prior art, since the spring 74 having a similar function to the pressure sensing spring 4 is disposed below the core iron portion (the first plunger piston 66 and the movable core 56), when the valve is started, neither the electromagnetic force nor the pressure of the suction port Ps can overcome the force of the spring 74, so that the second plunger 68 capable of engaging with the first plunger 66 is separately disposed, so as to be engaged with the spring 74 when the valve is started, so that the valve element 38 can move upward.

In the scheme, the pressure sensing spring 4 of the pressure sensing part is arranged in the coil shell 1 and is positioned above the core iron part, the transmission rod 11 is pressed, the transmission rod 11 drives the core iron 16 to push the valve core 21, so as to provide the original force for closing the valve core 21, when the compressor is just started, the electromagnetic suction force and the pressure of the suction inlet Ps can overcome the force of the pressure sensing spring 4 correspondingly, and the valve core 21 can move upwards smoothly so as to close the first valve port b. Obviously, in this embodiment, there is no need to provide a structure in which the second plunger 68 is disposed between the valve element 21 and the moving core 16, and the entire control valve structure can be further miniaturized, thereby promoting miniaturization of the entire compressor. It is understood that it is also possible to provide only the pressure-sensitive element in the coil housing 1, and the pressure-sensitive spring 4 below the moving core 16 and above the valve core 21 as the spring 74 in the related art.

In the present embodiment, the second valve port a is formed, and it should be understood that, in a cold environment or at night when the temperature difference is large, after the variable displacement compressor is stopped, the refrigerant gas is liquefied and accumulated in the crank chamber of the compressor. Just after the compressor is started, the compressor can only be operated at the minimum displacement before the crank chamber pressure drops to the prescribed pressure. Since the pressure in the crank chamber is a pressure generated by the vaporization of the refrigerant liquid stored in the crank chamber, the pressure in the crank chamber does not decrease until the refrigerant liquid is completely vaporized and discharged, and the discharge capacity is limited although the crank chamber communicates with the suction chamber through the fixed hole, so that the compressor cannot be operated in a set state for a long period of time after being discharged through the fixed hole. After the second valve port a is provided in this embodiment, when the compressor is just started, the liquid refrigerant can be quickly vaporized and then discharged from the suction port Ps, thereby realizing quick start.

in this embodiment, the second valve port a is formed by the position where the upper end of the valve element 21 is joined to the movable core 16, and in fact, the present embodiment only utilizes the valve element axial hole 21a through which the valve element 21 passes to realize the communication of the valve ports, so no matter what part the upper end of the valve element 21 is in contact with, the upper end of the valve element 21 and the upper end of the valve element can be separated at the time of the start of the compressor (in the background art, the second plunger 68 is separated from the operating rod 36 at the time of the start), and the second valve port b.

it should be noted that the control valve may be assembled as follows:

Forming the pressure sensing part (the pressure sensing shell 2, the supporting seat 3, the supporting rod 5, the pressure sensing spring 4, the pressure sensing diaphragm 8) and the core iron part (the static core iron 12, the movable core iron 16, the transmission rod 11, the core iron sleeve), installing the coil framework 14 wound with the enameled wire at the position of the static core iron 12 corresponding to the core iron part, nesting the magnetizer 7 on the pressure sensing shell 2, and integrally encapsulating and injecting to form the coil shell 1, i.e. the coil shell 1 is formed later, please refer to fig. 8 to understand, fig. 8 is a structural schematic diagram of the coil shell 1 in fig. 2 (only to more clearly illustrate the coil shell 1, actually the coil shell 1 is formed by injection molding and is integrated with the internal components thereof);

The valve body part and the coil part are connected through a connecting seat 18 (a third O-shaped ring 19 can be arranged on the periphery of the connecting seat 18 to isolate the suction port Ps from the external environment), in order to ensure the reliability of the position of the coil winding 13, a coil protective shell 17 is further arranged on the periphery corresponding to the coil shell 1, and the coil protective shell 17 can be made of soft magnetic materials and has the function of magnetic conduction to form a magnetic field loop with the connecting seat 18, the moving core iron 16, the static core iron 12, the magnetizer 7 and the like. Specifically, after the coil housing 1 is formed, the coil protecting shell 17 is nested and matched with the connecting seat 18, and then the matching position is welded, fixed and sealed. The fourth O-ring 6 may be inserted into a corresponding sealing groove of the coil housing 1 (to ensure the sealing between the inside and the outside of the coil portion), and then the coil housing 1 and the coil portion and the core iron portion inside the coil housing are integrally installed into the coil protecting case 17 until the end, and at this time, the second core iron sleeve 15 of the core iron sleeve is correspondingly inserted into the installation hole of the connecting seat 18. And then welding the matching part of the second core iron sleeve 15 and the connecting seat 18 to form fixing and sealing.

As can be seen from the above assembling process, the coil housing 1 in this embodiment is formed by injection molding after the coil winding 13, the core iron portion, and the pressure sensing portion are installed, so that the pressure sensing housing 2 is not only beneficial to forming a vacuum cavity and facilitating installation of the pressure sensing portion, but also beneficial to injection molding of the coil housing 1. Of course, when the forming process of the coil housing 1 is changed, the installation manner of the pressure sensing part may also be changed accordingly, for example, when the coil housing 1 is formed separately, the pressure sensing diaphragm 8 may also be directly installed in the top housing of the coil housing 1.

In addition, the pressure sensing element of the prior art is installed in the connecting member 48, and is limited by the volume of the connecting member 48, which is usually turned, and the size of the pressure sensing diaphragm 65 is limited; in this scheme, the coil housing 1 is formed by integral injection molding, and the pressure sensing element is installed in the pressure sensing housing 2 which can be formed by stretching, so the size of the pressure sensing element can be relatively larger, and larger effective induction displacement can be obtained.

Example 2

referring to fig. 9, fig. 9 is a schematic structural diagram of a second embodiment of a control valve of a variable displacement compressor according to the present invention, illustrating an operating state of the control valve when the compressor is turned off; fig. 10 is a schematic view of the valve body portion of fig. 9.

The control valve in this embodiment has a structure substantially identical to that in embodiment 1, except that the pressure-sensitive portions are provided differently, and the connection manner with the core sleeve is different.

The pressure sensing element of the pressure sensing part is specifically a corrugated pipe 8 ', and the structure of the pressure sensing part is changed correspondingly because the installation mode and the deformation mode of the corrugated pipe 8' are different from those of the pressure sensing film 8. The corrugated pipe 8 'does not need to be clamped, so the opening edge of the pressure sensing shell 2 can be directly butted and fixed with the core iron sleeve 15' of the core iron part without arranging an outer flanging structure for clamping.

In fig. 9, the pressure-sensitive case 2 also extends into the bobbin 14 (in embodiment 1, the pressure-sensitive case 2 is located above the bobbin 14 and is provided with a case flange), that is, the core portion is also partially located in the pressure-sensitive case 2. It is understood that, compared to embodiment 1, the portion of the lower end of the pressure-sensitive casing 2 extending into the bobbin 14 corresponds to the first core sleeve 9 in embodiment 1, and the core sleeve 15' in this embodiment corresponds to the second core sleeve 15 in embodiment 1. So set up, the actual installation of also being convenient for. Obviously, the core sleeve 15' can be designed to fully load the static core 12 and the moving core 16, and the axial length of the pressure-sensitive housing 2 can be shortened.

in addition, the upper end of the transmission rod 11 directly abuts against the lower side of the corrugated pipe 8 ', the upper side of the corrugated pipe 8' does not need the supporting rod 5 or the pressure sensing spring 4 in the embodiment 1 to abut against, and the upper side of the corrugated pipe can directly abut against the supporting seat 3 arranged at the top of the pressure sensing shell 2, so that the corrugated pipe 8 'and the pressure sensing spring 4 are guided and stabilized, the supporting seat 3 is provided with an extension rod extending downwards, and the corrugated pipe 8' and the pressure sensing spring 4 are both sleeved on the extension rod. When forming the pressure sensing portion, can weld bellows 8 ', pressure sensing spring 4 in supporting seat 3, the welding can be carried out under vacuum state for bellows 8 ' inner chamber after the welding is the vacuum cavity, and the concrete principle is the same as formation vacuum cavity in embodiment 1, also can eliminate the influence of air in the bellows 8 ' cavity to the deflection.

it can be seen that, in embodiment 2, only the pressure sensing diaphragm 8 is replaced by the bellows 8' in embodiment 1, and the installation structure is changed adaptively, and the specific working principle and process are completely consistent.

As can be appreciated in conjunction with fig. 9, 10 and 11-14, fig. 11 is a state of operation of the control valve of fig. 9 upon start-up of the compressor; FIG. 12 is a schematic view of the valve body portion of FIG. 11; FIG. 13 is a view showing an operation state of the control valve of FIG. 9 in a normal operation of the compressor; fig. 14 is a schematic view of the valve body portion of fig. 13.

when the compressor is not started:

When the coil is not electrified, the elastic force of the corrugated pipe (the corrugated pipe 8' and the pressure sensing spring 4) overcomes the resistance of the supporting spring 10 and the bottom spring 24, so that the transmission rod 11 and the movable core iron 16 are far away from the static core iron 12 to the maximum displacement position, the lower end part of the movable core iron 16 pushes the valve core 21 downwards, and the first valve port b is fully opened. At this time, the discharge port Pd and the crank chamber port Pc are communicated in the valve body 20.

When the compressor is started:

When the air temperature drops, the refrigerant in the crank chamber of the compressor is liquefied and accumulated. At this time, the compressor is started, the coil is electrified with large current to generate electromagnetic force, so that the moving core iron 16 approaches to the direction of the static core iron 12, at this time, the pressure of the suction port Ps is large, the pressure of the suction port Ps and the transmission rod 11 jointly push the corrugated pipe, the moving core iron 16 moves upwards for a certain distance and does not abut against the valve core 21, the valve core 21 moves in the same direction under the action of the bottom spring 24, so that the first valve port b is completely closed, the discharge port Pd is disconnected from the crank chamber port Pc, and the refrigerant in the discharge chamber cannot flow to the crank chamber.

the distance for moving the core iron 16 upwards needs to satisfy the following conditions: is disengaged from the valve spool 21, thereby opening the second port a to the maximum position. The suction port Ps communicates with the crank chamber port Pc, and the liquid refrigerant in the crank chamber is vaporized and flows into the suction chamber of the compressor through the crank chamber port Pc, the valve chamber, the axial hole of the valve element 21 through which the valve element 21 passes, the second valve port a, the valve chamber, and the suction port Ps. In the process of discharging the liquid refrigerant, the pressure of the suction chamber and the crank chamber gradually decreases, the pressure of the suction port Ps received by the corrugated pipe decreases, and the movable core iron 16 moves downwards along with the pressure. When the liquid refrigerant is discharged, the movable core iron 16 and the valve core 21 tightly abut again, and the second valve port a is closed.

The compressor is in a normal working state after being started:

In addition, when the current is constant, the bellows senses the pressure of the suction port Ps to control the opening degree of the first valve port b. When the refrigeration load becomes larger and the pressure of the suction port Ps becomes larger, the upward acting force applied to the bellows increases, the valve element 21 moves upward along with the core iron 16, the opening degree of the first valve port b becomes smaller, the refrigerant flowing into the crank chamber decreases, the discharge amount of the compressor increases, and the pressure of the suction port Ps gradually decreases to the set pressure. On the contrary, when the refrigeration load becomes smaller and the pressure of the suction port Ps becomes smaller, the upward acting force applied to the bellows is reduced, the valve element 21 moves downward along with the core iron 16, the opening degree of the first valve port b becomes larger, the refrigerant flowing into the crank chamber is increased, the discharge amount of the compressor is reduced, and the pressure of the suction port Ps is gradually increased to the set pressure.

the control valve in this embodiment may be assembled as follows:

The pressure-sensitive part (the support seat 3, the pressure-sensitive spring 4 and the bellows 8 ') and the core iron part (the static core iron 12, the movable core iron 16, the transmission rod 11 and the core iron sleeve 15') are formed. And winding an enameled wire on the coil skeleton 14, embedding the lower end of the pressure-sensitive shell 2 into a middle hole of the coil skeleton 14, nesting the magnetizer 7 on the pressure-sensitive shell 2, integrally encapsulating and injecting to form the coil shell 1, namely forming the integral coil part.

The valve body portion and the coil portion are connected by a connecting socket 18, and a coil protecting case 17 is provided. Specifically, after the coil housing 1 is formed, the coil protecting shell 17 is nested and matched with the connecting seat 18, and then the matching position is welded, fixed and sealed. Then, the pressure sensing part and the core iron part are nested in the connecting seat 18, the core iron sleeve 15 'is correspondingly embedded into the mounting hole of the connecting seat 18, and then the matching part of the core iron sleeve 15' and the connecting seat 18 is welded to form fixing and sealing. And the third O-shaped ring 6 is sleeved in a corresponding sealing groove of the coil shell 1, then the coil part is integrally installed in the coil protection shell 17 until the end, and the induction part and the core iron part are correspondingly embedded in the coil part.

the coil housing 1 in this embodiment can be injection molded before the pressure sensitive part is not assembled, since the support base 3 and the bellows 8' form a vacuum chamber.

in the embodiment 2, it should be emphasized that the pressure sensing element is a bellows 8 ', and based on the difference between the deformation of the pressure sensing diaphragm 8 and the pressure sensing spring 4, the pressure sensing spring of the embodiment 2 can be omitted, and the bellows 8' provides the force for closing the first valve port b. However, as described in embodiment 1, in order to avoid the influence of the air pressure, the inside of the bellows 8 ' is a vacuum environment, and if the pressure sensing spring 4 is not provided, when the compressor is not opened, the bellows 8 ' is compressed by the pressure of the suction port Ps from the outside in addition to the pre-compression providing the force for closing the first valve port b, and further pre-compression is generated, which reduces the service life of the bellows 8 '. Here, the pressure-sensing spring 4 is still provided, which is equivalent to the pressure-sensing spring 4 and the bellows 8 'together providing the force for closing the first valve port b, the precompression force of the pressure-sensing spring 4 is reasonably designed, and the bellows 8' can not deform or deform less when the compressor is not opened, so as to prolong the service life of the compressor.

as will be understood from embodiment 1, since the bellows 8' can directly provide the force for closing the first valve port b, the technical advantages of the first and second embodiments 1 can be achieved substantially simultaneously when the bellows is installed in the coil housing 1.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that it is obvious to those skilled in the art that various modifications and improvements can be made without departing from the principle of the present invention, and these modifications and improvements should also be considered as the protection scope of the present invention.

Claims

1. A control valve of a variable displacement compressor is provided with a valve body (20) which is provided with a suction inlet (Ps) communicated with a suction chamber of the compressor, a crank chamber port (Pc) communicated with a crank chamber, a discharge outlet (Pd) communicated with a discharge chamber of the compressor, and a first valve port (b) for communicating the discharge outlet (Pd) and the crank chamber port (Pc) when the control valve is opened;

The control valve is also provided with a pressure sensing part, a coil part and a core iron part, wherein the pressure sensing part comprises a pressure sensing element, and the pressure sensing element senses the pressure deformation of the suction port (Ps) and can drive a valve core (21) of the control valve to move so as to adjust the opening degree of the first valve port (b); the method is characterized in that:

The pressure-sensitive element is arranged in a coil housing (1) of the coil part;

The core iron part comprises a transmission rod (11) which is fixed with a movable core iron (16) of the core iron part and moves along the axial direction of the valve cavity, the transmission rod (11) is abutted against the pressure sensing element, the pressure sensing element deforms to drive the transmission rod (11) and the movable core iron (16) to move, and the movable core iron (16) drives the valve core (21) to move to adjust the opening degree of the first valve port (b);

One end of the valve core (21) facing the core iron part is directly jointed with a component on the valve core to form a second valve port (a);

The valve core (21) is provided with a valve core axial hole (21a), the valve core axial hole (21a) is a through hole, and when the valve core (21) is separated from a component positioned on the valve core (21), the second valve port (a) is opened to communicate the crank chamber port (Pc) and the suction port (Ps).

2. the control valve of a variable displacement compressor as claimed in claim 1, wherein the driving rod (11) and the moving core iron (16) are provided with a passage to communicate the suction port (Ps) and the pressure sensing element.

3. The control valve of a variable displacement compressor as claimed in claim 2, wherein the passage includes a first radial hole (16b) and a first axial hole (16a) communicating with each other and provided to the moving core iron (16), and a second radial hole (11b) and a second axial hole (11a) provided to the driving rod (11);

The first radial hole (16b) is positioned at one end of the movable core iron (16) close to the valve core (21) and communicated with the suction port (Ps) arranged on the valve body (20) in the radial direction; one end of the transmission rod (11) is inserted into the first axial hole (16a), and the second axial hole (11a) is communicated with the first axial hole (16 a); the second radial hole (11b) is formed in one end, which is abutted to the pressure sensing element, of the transmission rod (11).

4. the control valve of a variable displacement compressor as claimed in claim 1, wherein the pressure sensing member is a pressure sensing diaphragm (8).

5. The control valve of the variable displacement compressor as claimed in claim 4, wherein the pressure sensing part further comprises a pressure sensing housing (2), a core iron sleeve is further arranged in the control valve, the moving core iron (16) and the static core iron (12) of the core iron part are arranged in the core iron sleeve, the pressure sensing housing (2) is open at the lower part and is positioned in the coil housing (1), the core iron sleeve is provided with a sleeve flanging, the pressure sensing housing (2) is open and is provided with a housing flanging, and the periphery of the pressure sensing diaphragm (8) is clamped between the sleeve flanging and the housing flanging.

6. the control valve of a variable displacement compressor as claimed in claim 5, wherein the pressure sensing diaphragm (8) seals the opening of the pressure sensing housing (2), and the cavity of the pressure sensing housing (2) is formed as a vacuum chamber.

7. The control valve of a variable displacement compressor as claimed in claim 5, wherein a support rod (5) and a support seat (3) fixed to the top of the pressure sensing housing (2) are provided in the pressure sensing housing (2), a pressure sensing spring (4) is pre-compressed between the pressure sensing diaphragm (8) and the support seat (3), the pressure sensing spring (4) is sleeved on the support rod (5), the support rod (5) is axially movably inserted into the support seat (3), and the support rod (5) abuts against the pressure sensing diaphragm (8).

8. The control valve of a variable displacement compressor as claimed in claim 1, wherein the pressure sensing member is a bellows (8').

9. The control valve of the variable displacement compressor according to claim 8, wherein the pressure sensing portion further comprises a pressure sensing housing (2), the control valve is further provided with a core iron sleeve (15 '), the pressure sensing housing (2) is open at the lower part and is arranged in the coil housing (1), the corrugated pipe (8 ') is arranged at the top of the pressure sensing housing (2), the edge of the lower end opening of the pressure sensing housing (2) is butted with the edge of the core iron sleeve (15 '), and the movable core iron (16) and the static core iron (12) of the core iron portion are arranged in a mounting cavity formed after the butting.

10. The control valve of a variable displacement compressor as claimed in claim 9, wherein the inside of the bellows (8') is a vacuum chamber.

11. The control valve of a variable displacement compressor as claimed in claim 9, wherein a support seat (3) is provided at a top of the pressure sensing housing (2), the support seat (3) has an extension rod extending toward the core iron portion, and the bellows (8') is fitted over the extension rod.

12. The control valve of a variable displacement compressor as claimed in claim 8, wherein the pressure sensing portion further comprises a pressure sensing spring (4), the pressure sensing spring (4) being pre-compressed in the bellows (8') to abut against the transmission rod (11).